Piston pump



Aug. 1, 1939. c. GAUSMANN PISTON PUMP Filed Jan. l2, 1938 .Figi

/nventonj Patented Aug. l, 1939 .z ,aalzz Y P Is'roN r Carl Gausmann, Dessau, Anhalt, Germany, as.

signor to werke rlllztiengesellschaft, Dessau,

Germany Junkers Flugzeug-und-Motoren- Anhalt,

Application January 12, 1938, Serial No. 184,667

In Germany January 27, 1937 y 3 Claims.

` My invention relates to piston pumps and more especially to pumps for conveying liquids such as gasoline or the like, which have no lubricating action. In this type of pumps, in which the pis- 5 tons are reciprocated by means of a crank shaft, lubricant has been fed to the crank case under pressure for the purpose of lubricating the moving parts and of preventing non-lubricantliquid from entering the crank case. To this end the l0 crank case of the pump has been connected to a source of oil under pressure, for instance to the lubricant circulation of an internal combustion engine supplied by the pump with liquid fuel. In order to prevent oil from owing back from the 16 crank case of the pump and fuel from trickling through between the pump piston and the cylin der into the crank case and into the lubricant circulation of the engine, ywhen the pressure should drop in the lubricant feed pipe, for in- 20 stance when stopping the engine, a check valve of the disk valve type has been inserted between the crank case and the pressure oil feed. The use of such a check valvelis however inadvisable for the following reasons: The volume of the g5 crank case filled with voil under pressure does not remain constant during the operation of the pump, but changes in dependency -upon the position of the crank shaft. A similar change of Ivolume occurs not only in single piston pumps, but also, to a certain extent, in multi-piston pumps, the pistons ofwhich are connected to cranks arranged in uniform staggered relation, since for equal crank angles the distances traveled by the pistons during the working and return strokes are of different length. Consequently, when the volume of the crankcase is reduced. the lubricant in the crank.case has a tendency to ow back into the feed pipe, being however.

prevented from doing so by the'instantaneously 40 closing check valve which prevents its escape from the crank case. However since this oil is practically not compressible,I even slight changes of volume give rise to very high pressures which create a high power consumption ofthe pump and may in some cases even lead to destruction of the crank case. Apart therefrom the permanent opening and closing of a check valve of this kind in rapid succession leads to an early wear of the valve seat and requiresconstant repair. It is an object of this invention to provide means for avoiding the owing back of liquid from the crank case, supplied with oil under pressure. of piston pumps which does not involve the drawbacks mentioned above.

(c1. 1st-6) lmunicates with the crank case. 10

The chamber further communicates by means of another conduit with the crank case, this conduit being controlled by an edge of the piston in such manner thatgcommunication through this conduit is established whenever the pressure in l5 theliquid supply pipe, which acts on the piston,

is greater than both the pressure in the crank case and the force of the valve spring, the conduit being closed by the piston, whenever the latter combination of forces exceeds the pressure in the 30 supply pipe. f

In the drawings alxed to this specification and forming part thereof a twin piston pump embodying my invention is illustrated diagrammatically by way of example. 25

In the drawing Fig. 1 is an axial section on the line I-I in Fig. 2,`illustrating the means for preventing oil under pressure from flowing back from the crank v case in the operative position. 3o

Fig. la is another, illustration of a similar kind, but drawn to a slightly larger scale, of the same device, however in its position of rest.

Fig. 2 is a cross section of the pump on the line II-II in Fig. 1. l 35 Referring to the drawing, l is the circumferential wall and 2 and 3 the side walls forming the pump casing, 4 is the crank shaft, 5 and 6 the two pump pistons pivoted to this shaft and '1 and 8 are the roller-shaped cylinder bodies which 40 are located for angular reciprocation in a. hollow cylindrical cavity 9 of the circumferential wall l of the casing, which is closed in at each end by the side walls 2 and 3. These cylinder bodies are formed with diametrically extending borings, in 45 which the pistons 5 and 6 are free to reciprocate. In the wall of the cavity 9 are formed exhaust conduits Il and I2, respectively, for the liquid to be conveyed, these conduits being so arranged 4that when the pistons 5 and 6 are on 50` their outwardlstroke, the conduits Il, and during their inward stroke the exhaust conduits I2 are placed in communication with the working chamber of the pump. The crank shaft is accommodated in a cavity 9, the ends of the shaft being supported in bearings formed in the lateral walls 2 and 3, respectively. An extension I4 of the shaft projects through the wall 2, while a journal I5 at the other end is supported in the side wall 3. This wall is formed with a projection I6 formed with a cylindrical cavity I1 which is connected .at one end by means of` a. conduit I8 with the connecting branch I9 for the'oil feed 20, while its other end is connected by means of two conduits 2| and 22 with the crank case I0. The outer end 23 of conduit 22 is arranged in the wall of the cavity I1 between the ends of the conduits I8 and 2|. In the cavity I1 a piston 25'is located for reciprocation, its head being acted upon by the pressure in the oil feed 20, While its rear side is exposed to the' pressure in the crank case I0. At the end of the piston 25 facing the conduit I8 a valve dish 26 is formed which, when the piston is forced towards the conduit I8 by the pressure spring 28, which is inserted between the bottom 29 of the cavity and thebottom of the piston 25, can apply itself against the valve seat 3| provided at the top end 21 of the cavity I1 in such manner, that the inner end of the oil feed conduit I8 is covered.

The operation of this pump is as follows: Assumingfirst that there is no pressure in the feed pipel 20, then no pressure acts on the side of the piston 25 facing the top end 21 of the cavity I1, so that the spring 28 can shift the 'piston in the direction towards the end face 21 and can force the valve dish 26 onto its seat 3| (as shown in Fig. 1a). The piston now covers the opening- 23 of conduit 22. If pressure is now generated in the pipe 20, a force will act on the piston head, which -will 'ultimately overcome the pressure exerted by the spring 28 and will then force the piston 25 back into the position shown in Fig. 1', in which they control edge .30 of the piston uncovers the` inner end 23 of the conduit 22. Oil under pressure'can now flow through pipe 20, conduit I8, cavity I1 and conduit 22 into the crank case III, so that after a short period of time about the same pressure will prevail in the crank case IIJ-as in the pipe 20. If, during the operation of the pump, the volume of the crank case4 I8 changes and consequently'the pressure of the liquid in the crank case rises,l part of this liquid is rstforced out through the conduits 2| and 22. The liquid issuing from the conduit 22.\ flows through the cavity I1 and conduit |8 into the feed pipe 20 without being. able to bring about any material increase of pressure in the part of the cavity I 1 in front of the piston 25. In contradistinction thereto the liquid issuing fron/1 conduit 2 I into the part of the cavity I1 belovgdjhe piston 25 will cooperate with the spring 28 to force the piston towards the top end I1 of the cavity and the control edge 38 of the piston will now cover the inner opening 23 of conduit 22, so that now no liquid can iiow through this conduit into the which would be accompanied by an early wear and knocking of the` valve, the cavity is so dimensioned and the inner end 23 of conduit 22 so arranged that the volume of the part of cavity I1 which extends between the openings of the conduits I8 and 22, is larger than the volume of the quantity of liquid which, 0n the opening 23 being covered by the piston' 25, is expelled ,through the conduit 2| while the pump continues its operation. On thel crank shaft 4 continuing its rotatory movement,\,the volume of the crank case will rise again, so that the piston 25 is reversed again and the opening 23 uncovered. This play of the piston is repeatedin quick succession and only if the pressure in the feed pipe 28 disappears, for instance when th iinternal combustion engine driving the pump is stopped, the

piston will be shifted again bythe spring 28 into the position shown in Fig. 1a; f

I wish it to be understood that I do not desire to be limited to the exact details ofV construction shown and described for obvious modifications will occur toa person skilled in the art.

I claim: i l

1. Inv a pump in combination a pump casing,'a pump cylinder in said casing, a pump piston reciprocable in said pump cylinder, a crank shaft associated with said pump piston and a crank case accommodating said shaft, a valve chamber and two ax'ially spaced conduits connecting said chamber with said crank case, a liquid feed pipe and a feed conduit connecting said feed pipe with said valve chamber, a valve body forming a piston axially reciprocable in said valve chamber and adapted to control the connecting conduit adjoining said -feed conduit, a. spring tending to force said valve body towards and into closing position relative to said feed conduit and to the connecting conduit adjoining same, the volume of the part of said valve chamber extending between said feed conduit and the connecting conduit adjoining same being larger than the reduc tion of volume of the interior of the crank case resulting in the rotation of said crank shaft after said last mentioned connecting conduit has been 

